JPH02180376A - Hydraulic continuously variable transmission controller - Google Patents

Abstract

PURPOSE:To make it possible to constitute the controller in the title compact and to realize all sorts of control by mutually communicating oil routes of the plungers of the first rotary member and the plungers of a rotary members in a control system through pump ports provided on the second rotary member and fixed member. CONSTITUTION:The second rotary member 16 in a drive system for input or output so constituted as being coaxial with the first rotary member 10 in a drive system for input or output provided with a member of plungers 13 arranged therein and guiding the plungers 13 to a working surface 17a inclined by a specific angle to a surface which crosses the rotary shaft center at right angles is provided. Additionally, a rotary member 21 in a control system provided with a number of plungers 23 arranged around a rotary axial core coaxial and rotatable integrally with the first rotary member 10 and a fixed member 26 in a control system so constituted as guiding the plungers 23 of the rotary member 21 in the control system to and working surface 27a for making slant movement control at a variable angle to a surface which crosses a rotary axial core at right angles are provided. Then the oil routes 38, 39 of the plungers 13 in the control system and the plungers 23 are communicated together through pump ports 19, 20, 34 and 35 provided on the second rotary member 16 and the fixed member 26 respectively.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates primarily to a hydraulic continuously variable transmission control device for automobiles and the like.

(Prior art) As this type of hydraulic continuously variable transmission control device,
The one published in Publication No.-9665 is known.

In this case, a pump that performs a pump function by driving a plunger by rotation of a swash plate, a transmission device with a motor of the same configuration connected to this pump in a closed circuit, and a reaction torque generated within the pump are all driven shafts. It is equipped with another gear-type transmission device that recovers at the top, and transmits power from the drive shaft to the driven shaft in parallel.

(Problems to be Solved by the Invention) The hydraulic continuously variable transmission control device requires another gear-type transmission device, so the input and output shafts must be configured into two parallel shafts. Further, as in automobile travel control, consideration has not been given to direct drive in which the input and output shafts are driven at the same rotation, and overdrive in which the rotation of the output shaft is made higher than the rotation of the input shaft.

(Object of the Invention) The present invention has been made based on the above circumstances, and is capable of fully realizing hydraulic continuously variable speed without the aid of other gear-type speed change transmission devices. The present invention aims to provide a complete hydraulic continuously variable transmission control device that can perform output and speed change control and realize all controls such as forward/reverse rotation, deceleration, direct drive, and overdrive.

(Means for Solving the Problems) Therefore, in the present invention, a first rotary member of an input or output drive system in which a large number of plunger metals are arranged around a rotational axis, and a first rotary member coaxial with the first rotary member are provided. and a second rotating member k of an output or input drive system configured to guide the plunger on an operating surface inclined at a predetermined angle with respect to a plane perpendicular to the rotational axis, and coaxial with the first rotating member. A rotating member of a control system that is large and integrally rotatable and has a large number of plungers arranged around the rotation axis;
a fixed member of the control system having an operating surface whose tilt is controlled at a variable angle with respect to a plane orthogonal to the rotational axis, and configured to guide a plunger metal of the rotating member of the control system on the operating surface; A pump boat comprising: a pump boat provided on the second rotating member and the fixed member; The oil passages of the plunger of the first rotating member and the plunger of the rotating member of the control system are communicated directly through the first rotating member.

(Function) Therefore, structurally, all the components are arranged on one axis, so the overall structure can be compact, and since no separate transmission device such as a gear type is used, the structure is also single. Moreover, the reaction torque caused by the pump operation is also recovered to the output side, and the area of shift control in particular covers all controls such as forward/reverse, deceleration, direct drive, and overdrive, so it can be used for advanced control such as in automobiles. It can be adopted in the system.

(Example) The following is an example of the present invention? Referring to all the drawings, in the specific drawings, numerals 1 and 2 are frames of the transmission control device;
Rotating shaft 5'1f via bearings 3 and 4! - Pivotally supported. The rotating shaft 5 has a sleeve 6 that directly receives the bearing 3 fixed by a nut 7 screwed onto the rotating shaft 5, and also directly supports the bearing 4, so that the inner ring of the bearing 4 is fixed. The sleeve 8 is fitted into the rotary shaft 5, and the sleeve 8 is fixed with a nut 9 screwed onto the rotating shaft 5.

The rotary shaft 5 has a first drive system for output or input.
The rotating member IO is integrally constructed.

The rotating member 10 has a large number of cylinder holes 12 arranged in a predetermined pitch circle around the rotation axis, into which a plunger I3 is slidably fitted. In short, it is preferable that the plunger 13 and the cylinder hole 12 be in an oil-sealed state as much as possible. The cylinder holes 12 are bored into the rotating member lO through passages 14 extending in the radial direction, arranged on a pitch circle having a smaller diameter than the pitch circle described above. The second drive system for
A rotating member 16 is rotatably supported via a bearing llk. The second rotating member 16 rotatably supports an operating body 17 having an operating surface 17ar that is coaxial with the first rotating member IO and inclined at a predetermined angle with respect to a plane perpendicular to the rotational axis via a thrust bearing 18r. The outer end of the plunger 13 is still in contact with the operating surface 17aKVi. The second rotating member 16 also has the above-mentioned entrance/exit 15.
Corresponding to this, semi-arc shaped pump ports 19 and 20 are provided which are divided on the left and right sides in the direction of inclination of the operating surface 17a.

Furthermore, a control system rotating member 21 is integrally formed on the rotating shaft 5 together with the first rotating member lO. The rotating member 21 is coaxial with and rotatable integrally with the second rotating member 16, and similarly to the first rotating member 10 described above,
A large number of cylinder holes 22 are arranged in a circle with a constant pitch around one axis of rotation, and a plunger 23 is slidably fitted into each cylinder hole 22. Also, if necessary, the plunger 23 and the cylinder hole 22 may be sealed with oil as much as possible. The cylinder holes 22 are arranged through passages 24 extending in the radial direction on a pitch circle having a smaller diameter than the pitch circle described above.
It is connected to 5.

The frame 2 is integrally provided with a control system fixing member 26 so as to surround the rotation axis 5, and this fixation member 26 has tilting control at a variable angle with respect to a plane orthogonal to the rotation axis. The actuating body 27 is provided with an actuating surface 27a. The operating body 27 is a thrust bearing 28
? The control member 29 is rotatably supported by a control member 29, and the control member 29 is tiltably supported by the frame 2 about a pivot shaft 30 centered on the operating surface 27a. Further, the control member 29 is provided with a control pin 31,
The control rod 33 held between the control pin 3Lt and the fork 32 is connected to a control mechanism (not shown) so that the control rod 33 is controlled to move in the longitudinal direction of the rod. The plunger 23 is in contact with the operating surface 27a.

Furthermore, the fixing member 26 has a
It includes half-arc-shaped pump boats 34 and 35 that are divided on the left and right sides in the direction of inclination of the operating surface 27a.

The pump boat 34 is communicated with an annular passage 36 provided in the rotating shaft 5 through a through hole 34ai, and the pump boat 35 is connected to a through hole 35a? The annular passages 36 and 37 communicate with oil passages 38 and 39, respectively, through the annular passage 37 provided in the rotating shaft 5. On the other hand, the pump boat t9.20 also has an annular passage 3 provided in the rotating shaft 5 through the through holes 19a and 20a, respectively.
6x and 37X, respectively, and the annular passages 36X and 37x communicate with the oil passages 38 and 39, respectively.

Also, for the oil passages 38 and 39, check pulps 40 and 41. Hydraulic pressure for control is supplied from a hydraulic pump 44 through passages 42 and 43.

The hydraulic pump 44 communicates with the oil tank 45 on its suction side, and also communicates with the oil tank 45 on its delivery side, bypassing the pressure regulating valve 46. The control pressure of this pressure regulating valve 46 can be adjusted by a control system 47. Note that the above-mentioned rotating member I
The oil leaking out from the joint surface between the inlet and exit port [5] and the pump boats 19 and 20 of the rotating member 16 and the sliding part between the cylinder hole 12 and the plunger 13 is removed from the oil pan. The oil is recovered to the oil tank 45 via the oil tank 48. In addition, the above-mentioned entrance/exit 25 of the rotating member 21 and the pump boats 34 and 35 of the fixed member 26 are provided.
Similarly to the above, oil leaking from the joint surface between the cylinder hole 22 and the plunger 23 and the oil leaking from the sliding part between the cylinder hole 22 and the plunger 23 flows through the entire oil pan 48 to the oil tank. It will be collected on 45th.

In the figure, reference numeral 49 is an output or input gear provided on the first rotating member 10, and 50 is an input or output gear provided on the second rotating member 16.

In such a configuration, power is transmitted to the second rotating member 16 via the gear portion 50, for example, while the cylinder holes 12, 22 and the hydraulic paths connected thereto are filled with oil, and the hydraulic pressure is When the pump 44 is driven, the oil in the hydraulic path is maintained at the pressure value set by the pressure regulating valve 46, and when the second rotating member 16 rotates at the speed R, the oil in the hydraulic path is maintained at the pressure value set by the pressure regulating valve 46. Depending on the value of the inclination angle α, the first rotating member 10 will be rotated at a speed “.

As a result, torque is transmitted from the second rotating member 16 to the first rotating member 10 at the gear ratio a = r /R,
It is output via the gear section 49. - The point of generating such a gear ratio will be explained in detail below.

Now, each velocity kQr between the second rotating member 16 and the first rotating member IO and the pump discharge tQA by the first rotating member 10? I will consider it. When the second rotating member 16 does not rotate, that is, when r = Q, the second rotating member 1
6 rotates clockwise in FIG.
is pushed to obtain the pump discharge amount QA=Qk, and when the pump port is set to the 0 side, the plunger 13 is moved to the operating surface 17H.
, and obtain pump suction tQB=Q'e. If it is assumed that the first rotating member 10 is rotated at a speed r in the same direction as the second rotating member 16, the relative speed of both rotating members 16 and lO is (r), and the discharge on the pump port 19 side is The amount QA is QA=(1i')Q ・・・・・・+1) Similarly, the suction amount QA on the 0 side of the pump port is also approximately −r QA=()Q ・・・・・・(2) On the other hand , if the first rotating member 10 rotates at a speed r, the rotating member 21 of the control system rotates together with it, so the speed is r. Therefore, the plunger 23 follows the operating surface 27a of the fixed member 26, and the pump suction tQA''k is obtained on the pump boat 34 side, and the plunger 23 is pushed by the operating surface 27a, and the pump discharge amount QB is obtained on the pump port 35 side. If the pump flow rate Q'=kQ when the rotating member 21 rotates at the speed R, then the pump suction tQA' and the pump discharge t at the speed r
QB' is QA' = π・kQ (3) QB
'=1·kQ (4) In this case, k is the operating force for the discharge tQ determined by the inclination angle of the operating surface 17a when the second rotating member 16 and rotating member 21 have the same rotational speed. This is the ratio (coefficient a) of the discharge f#Q' determined by the inclination angle of the surface 27a.

From this, when the second rotating member 16 rotates at a speed tWi(+), in order for the first rotating member 10 to rotate at a speed "+", the pump boats 19 and 34 and the pump port must be set between 0 and 35 by pumping. , Q A = Q
A' and QB = Q B' oil flow is in oil passage 38
and 39.

From equations (1) and (3), ``QA=(-π-)・Q=QAl=(-Fll-,)・k
-Q From equations (2) and (4), - "QB=()・Q=QB'=(R)・k, QFrom the above equation,
k=(ur)/r (5) Now, the actuating body 27 is operated by the control rod 33, as shown in FIG. 6, its actuating surface 27a? When tilting at an inclination angle α, if k=l, then = i=(R-r)/r Therefore, r=R/2 When the second rotating member 16 rotates at a speed of As such, when the operating surface 27a k inclination angle α=0,
QA'=O Therefore, in order for QA=0, the second
The rotating member 16 and the first rotating member 10 are in a coupled state, resulting in a direct transmission. This shows the case where =o.

Similarly, if O<k<1, then the relationship rFi (r<ty2) is established.

If k)l, that is, Q'>Q, in this embodiment, when the inclination angle α' of the inclined surface 17a and the inclined surface α>α' of the inclined surface 27a, r < ) l, /2.

Incidentally, if Q'=2Q (in this example, sin α=
sin2αl), “=V3.

When expecting overdrive, it is necessary to set k<0. That is, the inclination angle α of the operating surface 27a exceeds the plane orthogonal to the rotation axis S and takes an angle Of with a negative sign.

In the above embodiment, the gear portion 49 may be used as an input portion, and the gear portion 50 may be used as a purple output portion. In this case, the pump ports 0 and 34 are on the discharge side, and the pump boats 19 and 35 are on the suction side (assuming the same direction of rotation as in the previous embodiment). Further, the tilt angle of the tilt body 27 is on the negative side. That is, when the first rotating member 10 rotates at a speed r and the second rotating member 16 rotates at a speed r, suction tQB=()Q is obtained from the pump port 0 and the discharge ratio -r-to 19. At this time,
When the rotating member 21 of the control system is rotated at the speed R, the pump boat 34 obtains a suction t Q A'=kQ, while the pump boat 35 obtains a discharge amount Q 13'=k Q.

QA: QA' and Q B = Q B/k from the above formula
= (R-r)/R From this, when = 1, that is, when Q' = Q, the second
The rotating member 16 is not driven at r=Q even if the first rotating member 10 rotates at a constant speed.

Also, when k=0, that is, QA=QA'=O1Q 1
3 = Q B' = O, the first rotating member 10 and the second rotating member 16 are in a coupling state, and k = r
It is.

If O<k('l, then r>r>0.

If you want to expect an overdrive, you need to set k(O. Also, if you want to expect a reversal, you need to set k>r.

In the above embodiment, reference numeral 51 indicates a thrust bearing provided between the frame 1 and the second rotating member 16, and reference numeral 52 indicates a thrust bearing provided between the frame 2 and the sleeve 8.

In addition, in the above embodiment, the operating surface! 78 or operating surface 27
Although the configuration is such that the plungers 13 and 23 are simply brought into contact with the actuating body 17 and 27 using links, each plunger 13 or 23? Of course, a structure in which they are pivotally connected may also be used. The operating surfaces L7a, 27a referred to here refer to functional slopes that guide the plunger 13.23 to perform pump action.
It is not structurally restricted.

Further, in this embodiment, the actuating surfaces L7a and 27ak are formed on the actuating body 17.27, respectively, and the actuating body 17.27 is rotatably supported by the second rotating member 16 and the control member 29, but directly, Of course, it may also be formed on the second rotating member 16 and the control member 29.

In addition, hydraulic pressure is supplied from the hydraulic pump 44 to the second rotating shaft 5rr:
Although the supply is carried out via the supply route, it is of course possible to supply the supply from other suitable locations.

In the embodiment shown in FIGS. 8 and 9, the first rotating member lO
and the pump structure of the rotating member 21 of the control system? This is a structure in which the axial length is shortened by arranging them alternately.

In this case, the total number of plungers 13 and 23 is half that of the previous embodiment.

(Effects of the Invention) The present invention has been described in detail above, and a hydraulic continuously variable transmission can be realized without the aid of any other gear-type transmission. Moreover, it is a -axis arrangement, with a first rotating member of the drive system, a second rotating member of the coaxial center, a rotating member of the control system that is integrated with the first rotating member, and a fixed member? A swash plate pump structure and a variable swash plate pump structure arranged on the same axis and configured between them realize stepless speed change, and high efficiency speed change control that allows reaction torque generated in the pump to be recovered to the driven member. It is a device.

In addition, by considering all inputs and outputs, the speed change range can be selected according to the application, and control such as forward/reverse rotation, deceleration, direct drive, and overdrive can be realized.

In particular, in the present invention, since the control section of the variable swash plate is located on the fixed member side, it is easy to completely simplify the control form of the operating surface (variable swash plate). Also, on the first rotating member and the rotating member of the control system? Since it is configured to rotate integrally, two sets of plunger type pump structures can be incorporated into one configuration, so the overall structure can be made compact.

[Brief explanation of the drawing]

Is Figure 1 an example of the invention? 2 to 5 are sectional views taken along lines II-II to VV in FIG. 1, FIG. 6 is a longitudinal sectional side view for explaining the entire control operation, and FIG. The front view of the control member, FIGS. 8 and 9, are a vertical side view and a vertical front view of another embodiment. 10...First rotating member 12...Cylinder hole"3
...Plunger 15...Entrance/exit 16...Second
Rotating member 17... Operating body 17a... Operating surface
19.20...Pump port 1...Rotating member (control system) 22...Cylinder hole 23...Plunger 25...Inlet/outlet 26...Fixing member 27...
- Operating body 27... Operating surface 29... Control member
34.35...Pump boat patent applicant A. Take

Claims (1)

[Claims] A first rotating member of an input or output drive system in which a large number of plungers are arranged around the rotational axis, and a first rotating member that is coaxial with the first rotating member and tilted at a predetermined angle with respect to a plane orthogonal to the rotational axis. a second rotary member of the output or input drive system configured to guide the plunger in the operating plane thereof; and a second rotary member of the drive system for output or input configured to guide the plunger; The rotating member of the control system is provided with a large number of plungers, and the actuating surface is tilted at a variable angle with respect to a plane orthogonal to the axis of rotation. a fixed member of the control system configured to guide the plunger, and the plunger of the first rotating member and the plunger of the rotating member of the control system are connected to each other through pump ports provided in the second rotating member and the fixed member. A hydraulic continuously variable transmission characterized by having two oil passages in communication with each other.